Lean burn internal combustion engine exhaust gas temperature control

ABSTRACT

A variety of methods and arrangements for controlling the exhaust gas temperature of a lean burn, skip fire controlled internal combustion engine are described. In one aspect, an engine controller includes an aftertreatment system monitor and a firing timing determination unit. The aftertreatment monitor obtains data relating to a temperature of one or more aftertreatment elements, such as a catalytic converter. Based at least partly on this data, the firing timing determination unit generates a firing sequence for operating the engine in a skip fire manner such that the temperature of the aftertreatment element is controlled within its effective operating range.

CROSS REFERENCE TO RELATED APPLICATIONS

This application is a Continuation of U.S. application Ser. No. 15/347,562, filed on Nov. 9, 2016, which claims priority to U.S. Provisional Application No. 62/254,049, filed on Nov. 11, 2015, both of which are incorporated by reference herein in their entirety for all purposes.

FIELD OF THE INVENTION

The present invention relates to a skip fire engine control system for an internal combustion engine. More specifically, the present invention relates to arrangements and methods for controlling exhaust gas temperature to improve efficacy of an emission control system.

BACKGROUND

Most vehicles in operation today are powered by internal combustion (IC) engines. Internal combustion engines typically have multiple cylinders or other working chambers where combustion occurs. The power generated by the engine depends on the amount of fuel and air that is delivered to each working chamber. The engine must be operated over a wide range of operating speeds and torque output loads to accommodate the needs of everyday driving.

There are two basic types of IC engines; spark ignition engines and compression ignition engines. In the former combustion is initiated by a spark and in the latter by a temperature increase associated with compressing a working chamber charge. Compression ignition engines may be further classified as stratified charge compression ignition engines (e.g., most conventional Diesel engines, and abbreviated as SCCI), premixed charge compression ignition (PCCI), reactivity controlled compression ignition (RCCI), gasoline compression ignition engines (GCI or GCIE), and homogeneous charge compression ignition (HCCI). Some, particularly older, Diesel engines generally do not use a throttle to control air flow into the engine. Spark ignition engines are generally operated with a stoichiometric fuel/air ratio and have their output torque controlled by controlling the mass air charge (MAC) in a working chamber. Mass air charge is generally controlled using a throttle to reduce the intake manifold absolute pressure (MAP). Compression ignition engines typically control the engine output by controlling the amount of fuel injected (hence changing the air/fuel stoichiometry), not air flow through the engine. Engine output torque is reduced by adding less fuel to the air entering the working chamber, i.e. running the engine leaner. For example, a Diesel engine may typically operate with air/fuel ratios of 20 to 55 compared to a stoichiometric air/fuel ratio of approximately 14.5.

Fuel efficiency of internal combustion engines can be substantially improved by varying the engine displacement. This allows for the full torque to be available when required, yet can significantly reduce pumping losses and improve thermal efficiency by using a smaller displacement when full torque is not required. The most common method today of implementing a variable displacement engine is to deactivate a group of cylinders substantially simultaneously. In this approach the intake and exhaust valves associated with the deactivated cylinders are kept closed and no fuel is injected when it is desired to skip a combustion event. For example, an 8 cylinder variable displacement engine may deactivate half of the cylinders (i.e. 4 cylinders) so that it is operating using only the remaining 4 cylinders. Commercially available variable displacement engines available today typically support only two or at most three displacements.

Another engine control approach that varies the effective displacement of an engine is referred to as “skip fire” engine control. In general, skip fire engine control contemplates selectively skipping the firing of certain cylinders during selected firing opportunities. Thus, a particular cylinder may be fired during one engine cycle and then skipped during the next engine cycle and selectively skipped or fired during the next. In this manner, even finer control of the effective engine displacement is possible. For example, firing every third cylinder in a 4 cylinder engine would provide an effective reduction to ⅓^(rd) of the full engine displacement, which is a fractional displacement that is not obtainable by simply deactivating a set of cylinders to create an even firing pattern.

Both spark ignition and compression ignition engines require emission control systems including one or more aftertreatment elements to limit emission of undesirable pollutants that are combustion byproducts. Catalytic converters and particulate filters are two common aftertreatment elements. Spark ignition engines generally use a 3-way catalyst that both oxidizes unburned hydrocarbons and carbon monoxide and reduces nitrous oxides (NO_(x)). These catalysts require that on average the engine combustions be at or near a stoichiometric air/fuel ratio, so that both oxidation and reduction reactions can occur in the catalytic converter. Since compression ignition engines generally run lean, they cannot rely solely on a conventional 3-way catalyst to meet emissions regulations. Instead they use another type of aftertreatment device to reduce NO_(x) emissions. These aftertreatment devices may use catalysts, lean NO_(x) traps, and selective catalyst reduction (SCR) to reduce nitrous oxides to molecular nitrogen. The most common SCR system adds a urea/water mixture to the engine exhaust prior to the engine exhaust flowing through a SCR based catalytic converter. In the SCR element the urea breaks down into ammonia, which reacts with nitrous oxides in the SCR to form molecular nitrogen (N₂) and water (H₂O). Additionally, Diesel engines often require a particulate filter to reduce soot emissions.

To successfully limit engine emissions all aftertreatment system elements need to operate in a certain elevated temperature range to function more efficiently. Since 3-way catalysts are used in spark ignition engines where the engine air flow is controlled, it is relatively easy to maintain a sufficiently elevated engine exhaust temperature, in the range of 400 C, to facilitate efficient pollutant removal in a 3-way catalyst. Maintaining adequate exhaust gas temperature in a lean burn engine is more difficult, since exhaust temperatures are reduced by excess air flowing through the engine. There is a need for improved methods and apparatus capable of controlling the exhaust gas temperature of a lean burn engine over a wide range of engine operating conditions.

SUMMARY OF THE INVENTION

A variety of methods and arrangements for heating or controlling a temperature of an aftertreatment element in an exhaust system of a lean burn internal combustion engine are described. In one aspect, an engine controller includes an aftertreatment element monitor and a firing timing determination unit. The aftertreatment element monitor is arranged to obtain data relating to a temperature of one or more aftertreatment elements, such as a catalytic converter. This data may be in the form of an aftertreatment element temperature model and/or may involve a direct measurement or sensing of the temperature of the aftertreatment element. The firing timing determination unit determines a firing sequence for operating the working chambers of the engine in a skip fire manner. The firing sequence is based at least in part on the aftertreatment element temperature data.

Some implementations involve a skip fire engine control system that dynamically adjusts the firing fraction or firing sequence in response to a variety of conditions and engine parameters, including oxygen sensor data, NO_(x) sensor data, exhaust gas temperature, barometric pressure, ambient humidity, ambient temperature and/or catalytic converter temperature. In various embodiments, the firing sequence is determined on a firing opportunity by firing opportunity basis.

In another aspect a method of operating a lean burn internal combustion engine having a plurality of working chambers during a cold start is described. The method includes deactivating at least one working chamber such that no air is pumped through the working chamber, obtaining data relating to a temperature of an element in an aftertreatment system, and determining a firing sequence for operating the working chambers of the engine in a skip fire manner. The firing sequence is generated at least in part based on the aftertreatment temperature data.

BRIEF DESCRIPTION OF THE DRAWINGS

The invention and the advantages thereof, may best be understood by reference to the following description taken in conjunction with the accompanying drawings in which:

FIG. 1A is a schematic diagram of a representative engine exhaust system for an exemplary compression ignition engine.

FIG. 1B is a schematic diagram of an alternative representative engine exhaust system for an exemplary compression ignition engine.

FIG. 2 is a plot of exhaust gas temperature versus engine load for an exemplary compression ignition engine.

FIG. 3 is a skip fire engine controller according to a particular embodiment of the present invention.

FIG. 4 is a plot of exhaust gas temperature versus engine load for an exemplary compression ignition engine operating under skip fire control with skipped cylinders being deactivated.

FIG. 5 is a plot of exhaust gas temperature versus engine load for an exemplary compression ignition engine operating under skip fire control with skipped cylinders pumping air.

FIG. 6 is a prior art representative plot of an aftertreatment element temperature during a cold start-up and over a portion of a drive cycle.

FIG. 7 is a representative plot of an aftertreatment element temperature during a cold start-up and over a portion of a drive cycle using skip fire control.

In the drawings, like reference numerals are sometimes used to designate like structural elements. It should also be appreciated that the depictions in the figures are diagrammatic and not to scale.

DETAILED DESCRIPTION

The present invention relates to a skip fire engine control system for an internal combustion engine—and particularly, lean burn internal combustion engines. More specifically, the present invention relates to arrangements and methods for controlling exhaust gas temperature to improve efficacy of an emission control system. In various embodiments, the firing sequence is determined on a firing opportunity by firing opportunity basis or using a sigma delta, or equivalently a delta sigma, converter. Such a skip fire control system may be defined as dynamic skip fire control.

Skip fire engine control contemplates selectively skipping the firing of certain cylinders during selected firing opportunities. Thus, for example, a particular cylinder may be fired during one firing opportunity and then may be skipped during the next firing opportunity and then selectively skipped or fired during the next. This is contrasted with conventional variable displacement engine operation in which a fixed set of the cylinders are deactivated during certain low-load operating conditions. In skip fire operation the firing decisions may be made dynamically; for example, on a firing opportunity by firing opportunity basis although this is not a requirement.

Skip fire engine control can offer various advantages, including substantial improvements in fuel economy for spark ignition engines where pumping losses may be reduced by operating at higher average MAP levels. Since compression ignition engines do not typically run at low manifold pressures, skip fire control does not offer a significant reduction in pumping losses for this type of engine. It does however provide a means to control the engine exhaust gas temperature over a wide range of engine operating conditions. In particular, skip fire control may be used to increase exhaust gas temperature such that it is generally maintained in a range where aftertreatment emission control systems can efficiently reduce tailpipe emissions. Skip fire control can offer a 10% improvement in efficiency in compression ignition engines at light loads; for example, loads under 1 bar BMEP (Brake Mean Effective Pressure).

FIG. 1A is a schematic diagram of an exemplary lean burn engine and exhaust system. An engine 111 has a number of working chambers or cylinders 114 where combustion occurs. Exhaust gases from the combustion process leave the cylinders 114 by way of an exhaust manifold 102. An exhaust system 103 a includes one or more aftertreatment elements to reduce emission of noxious material into the environment. These elements may include a particulate filter 104, an oxidizing catalytic converter 106, a reduction agent injection system 108, and a reducing catalytic converter 113. Collectively these various aftertreatment elements or devices may be referred to as an aftertreatment system. The particulate filter 104 removes particulate matter, i.e. soot, which may be present in the exhaust stream. The oxidizing catalytic converter 106 oxidizes unburned hydrocarbons and carbon monoxide in the exhaust stream. Since the engine 111 is generally operating with a lean air/fuel ratio there is generally adequate oxygen in the exhaust stream to oxidize these incomplete combustion products. The reduction agent injection system 108 introduces a reducing agent, often a mixture of urea and water into the waste stream. The reducing catalytic converter 113 may use selective catalytic reduction (SCR) to reduce nitrous oxides to molecular nitrogen and water. The reducing catalytic converter 113 may use two catalysts. A first catalyst 110 to transform urea in the reducing agent 108 to ammonia and a second catalyst 112 to transform nitrous oxides and ammonia into molecular nitrogen and water. After passing through the reducing catalytic converter 113, the exhaust stream leaves the exhaust system 103 a via tailpipe 124 and goes into the environment. The various aftertreatment elements in the exhaust system 103 a may sufficiently remove noxious pollutants from the exhaust stream such that it is compatible with current environmental regulations.

The exhaust system 103 a may additionally include one or more sensors. For example, oxygen sensors 109 a and 109 b may be placed before and after the oxidizing catalytic converter 106, respectively. A NO_(x) sensor 117 may be situated downstream from the reducing catalytic converter 113. One or more temperature sensors may also be incorporated in the exhaust system 103 a. Specifically, there may be a temperature sensor 107 to monitor the temperature of oxidizing catalytic converter 106, a temperature sensor 105 to monitor the temperature of the particulate filter 104, and a temperature sensor 115 to monitor the temperature of the reducing catalytic converter 113. Additional sensors (not shown in FIG. 1A or 1B), such as a temperature sensor in the exhaust manifold may be incorporated into the exhaust system.

In order for the aftertreatment elements in an exhaust system to properly function, they need to operate in a certain elevated temperature range. In particular, the catalysts in both the oxidizing catalytic converter 106 and the reducing catalytic converter 113 need to operate over a relatively narrow temperature range. A representative operating range for the reducing catalyst may be between 200 and 400 C, although other catalysts may have different ranges. The oxidizing catalyst may have a broader and somewhat higher operating range. Placement of the oxidizing catalyst upstream from the reducing catalyst results in the oxidizing catalyst being generally exposed to higher temperature exhaust gases, since there is less time for the gases to cool in the exhaust system. Generally, aftertreatment elements in the exhaust system may be arranged such that elements with higher operating temperature ranges are closer to the engine than the other elements. This allows the first aftertreatment element, for example, the particulate filter 104 in FIG. 1A, to experience the highest temperature exhaust stream. The exhaust stream will generally cool as it passes through subsequent elements in the exhaust path unless significant energy is released in any of the aftertreatment devices from exothermic chemical reactions, from an external heat source, oxidization of uncombusted hydrocarbons, or from some other heat source.

The temperature of an aftertreatment element will generally be close to that of the exhaust gas passing through it, although in some cases exothermic chemical reactions facilitated by a catalyst may increase its temperature. Generally exhaust gases will cool as they pass through the exhaust system due to heat transfer from the exhaust system elements and piping into the environment, although continued oxidization of uncombusted or partially combusted fuel may increase the exhaust gas temperature. This oxidation may occur both in the exhaust gas stream or on the oxidizing catalyst. The mass of the aftertreatment system catalysts are also relatively large compared to the mass flow rate of exhaust gases through the catalysts, thus it typically takes several minutes for the catalysts' temperature to equilibrate to that of the exhaust gas flowing through it.

It should be appreciated that the order of the elements in the aftertreatment system may be modified. The arrangement shown in FIG. 1A may be appropriate for systems where the particulate filter 104 does not require an active cleaning or regeneration process. FIG. 1B shows an alternative representative exhaust system 103 b. A difference between this system and the exhaust system 103 a shown in FIG. 1A is the order of the various aftertreatment elements in the exhaust stream. In FIG. 1B the oxidizing catalytic converter 106 is placed upstream of the particulate filter 104. This arrangement may be advantageous when the particulate filter 104 needs to be regularly cleaned by an active process that raises its temperature to around 500 C to 600 C to burn out accumulated soot on the particulate filter 104. The active cleaning process may include introducing uncombusted hydrocarbons into the exhaust stream and converting them into heat by oxidizing them in the oxidizing catalytic converter 106. By positioning the oxidizing catalytic converter 106 upstream from the particulate filter 104, the particulate filter temperature may be actively controlled during the cleaning process. Alternatively, the particulate filter 104 may be situated downstream of the reducing catalytic converter 113. The order of the aftertreatment elements may vary depending on their operating temperature ranges and maximum allowable temperatures.

Various other features and elements not shown in FIGS. 1A and 1B may be incorporated into the exhaust system. Such elements may include, but are not limited to, an exhaust gas recirculation system (EGR), a turbine to power a turbocharger, and a waste gate to control exhaust gas flow through the turbine.

FIG. 2 shows exhaust gas temperature at the exhaust manifold (102 in FIGS. 1A and 1B) versus engine operating load for a representative boosted, compression ignition engine operating at 1250 rpm. The curve 280 represents the exhaust gas temperature as a function of engine load expressed in Brake Mean Effective Pressure (BMEP) for a case where all engine cylinders are firing under substantially the same conditions. The engine output is generally controlled by varying the amount of injected fuel, although other engine parameters such as fuel injection timing and exhaust gas recirculation may impact engine output. The highest output load is associated with a stoichiometric air fuel ratio, where substantially all oxygen in the air charge is consumed during combustion. Lower output loads correspond to leaner air/fuel ratios and changing the timing of the fuel injection. Also shown in FIG. 2 as shaded area 270 is an operating temperature range for the engine exhaust temperature that enables efficient aftertreatment operation. The effective temperature range may be limited by the SCR catalyst in the reducing catalytic converter 113, which often has a more limited operating temperature range than oxidizing catalysts and particulate filters. The shaded area 270 depicted in FIG. 2 has an operating range of about 200 C, which is a typical value. The SCR catalyst needs to be maintained within this temperature range for the aftertreatment system to efficiently remove NO_(x) from the exhaust stream. In some cases if the SCR catalyst is within its operating temperature range, then the other aftertreatment elements are within their respective operating ranges. In this case the temperature operating range of the SCR catalyst represents the temperature operating range of the entire aftertreatment system. If other aftertreatment elements in the exhaust system have different or narrower operating temperature ranges the operating temperature range 270 depicted in FIG. 2 may need to be modified.

It should be appreciated that the operating range 270 depicted in FIG. 2 is not necessarily the operating temperature range of the catalyst, but is the temperature range of exhaust gases in the exhaust manifold that result in the catalyst being in its operating temperature range. For example, the SCR catalyst operating temperature range may be 200 to 400 C and the exhaust gases may cool by 25 C prior to reaching the catalyst. Thus the shaded area 270 represents an exhaust gas temperature range of approximately 225 to 425 C. Different engine operating points and engine designs may have different steady-state offsets between the exhaust gas temperature and temperature of the SCR catalyst or other catalysts in the aftertreatment system. In some cases the exhaust gas temperatures may rise in the exhaust system due to exothermic chemical reactions. The values given above for the catalyst temperature operating range and offset temperature between the catalyst and exhaust manifold gas temperature are representative only and should not be construed as limiting the scope of the present invention.

Inspection of FIG. 2 indicates that only over about half of the engine operating range do exhaust gas temperatures fall within an acceptable range for effective NO_(x) removal. Advantageously, skip fire engine control may be used to control exhaust gas temperature over most of an engine operating load range experienced in a typical driving cycle so that the aftertreatment system temperature remains within its operating temperature window. In particular deactivating one or more cylinders, such that no air is pumped through a cylinder during an operating cycle, increases the average temperature of the exhaust gases exiting the engine. A cylinder may be deactivated by deactivating the cylinder intake(s) valves, the cylinder exhaust valve(s) or both intake and exhaust valves(s). Effectively shutting off a cylinder results in less air to dilute the hot exhaust gases generated by combustion. In particular skip fire control may be used to raise the temperature of the exhaust stream under low load conditions.

Referring initially to FIG. 3, a skip fire engine controller 200 in accordance with one embodiment of the present invention will be described. The engine controller 200 includes a firing fraction calculator 206, a firing timing determination unit 204, a power train parameter adjusting module 216, a firing control unit 240 and an aftertreatment monitor 202. The firing control unit 240 receives input from the firing timing determination unit 204, the aftertreatment monitor 202, and the power train parameter adjusting module 216 and manages operation of the working chambers of an engine based on that input.

The aftertreatment monitor 202 represents any suitable module, mechanism and/or sensor(s) that obtain data relating to a temperature of an aftertreatment element. It may correspond to the temperature of reducing catalytic converter 113, oxidizing catalytic converter 106, or particulate filter 104 (see in FIGS. 1A and 1B). If the reducing catalytic converter has the narrowest operating range of any aftertreatment element, only data representative of its temperature may be used. In various embodiments, for example, the aftertreatment monitor 202 may include oxygen sensor data from oxygen sensors 109 a and/or 109 b. Aftertreatment monitor may also include measurements from NO_(x) sensors placed before and after the reducing catalytic converter 113. Aftertreatment monitor 202 may also include such inputs as ambient air temperature, exhaust gas temperature in the exhaust manifold, barometric pressure, ambient humidity and/or engine coolant temperature. Temperature data may be obtained using one or more sensors, such as temperature sensors 105, 107 and 115. In some embodiments, the engine controller 200 and the aftertreatment monitor 202 do not require a direct measurement or sensing of the temperature of an aftertreatment element. Instead, an algorithm using one or more inputs, such as a catalytic converter temperature model, may be used to determine the aftertreatment element or system temperature. The model is based on one or more of the above parameters (e.g., oxygen sensor data, NO_(x) sensor data, exhaust gas temperature, ambient temperature, barometric pressure, ambient humidity, etc.) that are representative or related to a catalytic converter temperature. In some embodiments a combination of a temperature model may be combined with measured temperature values to determine the temperature data. In particular, the model may be used to predict aftertreatment element temperature in transient situations, like engine startup or transitions between engine loads. A feed forward based control system may be used to control the temperature of an aftertreatment element in such cases. In still other embodiments, the aftertreatment monitor 202 directly estimates or senses the catalytic converter temperatures or temperatures of other elements in the aftertreatment system. The aftertreatment monitor 202 transmits the aftertreatment system temperature data to the power train parameter adjusting module 216, the firing timing determination unit 204, the firing control unit 240 and/or the firing fraction calculator 206.

In addition to the aftertreatment monitor temperature data, the firing fraction calculator 206 receives input signal 210 that is indicative of a desired torque or other control signal. The signal 210 may be received or derived from an accelerator pedal position sensor (APP) or other suitable sources, such as a cruise controller, a torque controller, etc.

Based on the above inputs, the firing fraction calculator 206 is arranged to determine a skip fire firing fraction (i.e., commanded firing fraction 223). The firing fraction is indicative of the percentage of firings under the current (or directed) operating conditions that are required to deliver the desired output and aftertreatment element temperature. Under some conditions, the firing fraction may be determined based on the percentage of optimized firings that are required to deliver the desired output and aftertreatment element temperature (e.g., when the working chambers are firing at an operating point substantially optimized for fuel efficiency). It should be appreciated that a firing fraction may be conveyed or represented in a wide variety of ways. For example, the firing fraction may take the form of a firing pattern, sequence or any other firing characteristic that involves or inherently conveys the aforementioned percentage of firings.

The firing fraction calculator 206 takes into account a wide variety of parameters that might affect or help indicate the aftertreatment element temperature. That is, the firing fraction is determined at least partly based on the aftertreatment element temperature data received from the aftertreatment monitor 202. In some approaches, the firing fraction is based on direct measurement of the aftertreatment element. Additionally, other information may be used to determine the firing fraction, for example, oxygen sensor data, NO_(x) sensor data, ambient air temperature, exhaust gas temperature, catalyst temperature, barometric pressure, ambient humidity, engine coolant temperature, etc. In various embodiments, as these parameters change with the passage of time, the firing fraction may be dynamically adjusted in response to the changes.

The method used to generate the firing fraction may vary widely, depending on the needs of a particular application. In one particular approach, the firing fraction is generated at least partly as a function of time. That is, a preliminary firing fraction value is generated that is adjusted in a predetermined manner depending on the amount of time that has passed since engine startup. The preliminary value may then be adjusted further using an algorithm based on any of the above parameters, such as ambient air temperature, exhaust gas temperature, catalyst temperature, NO_(x) sensor data, and/or oxygen sensor data. In various embodiments, some firing fractions are known to cause undesirable noise, vibration and harshness (NVH) in particular vehicle or engine designs, and such firing fractions may be adjusted or avoided. In still other embodiments, a firing fraction is selected based on aftertreatment element temperature data from a predefined library of firing fractions that have acceptable NVH characteristics. The aftertreatment element temperature data may be obtained from an aftertreatment element temperature model or may be a sensed aftertreatment element temperature.

In the illustrated embodiment, a power train parameter adjusting module 216 is provided that cooperates with the firing fraction calculator 206. The power train parameter adjusting module 216 directs the firing control unit 240 to set selected power train parameters appropriately to insure that the actual engine output substantially equals the requested engine output at the commanded firing fraction. By way of example, the power train parameter adjusting module 216 may be responsible for determining the desired fueling level, number of fuel injection events, fueling injection timing, exhaust gas recirculation (EGR), and/or other engine settings that are desirable to help ensure that the actual engine output matches the requested engine output. Of course, in other embodiments, the power train parameter adjusting module 216 may be arranged to directly control various engine settings.

In some implementations of the present invention, the power train parameter adjusting module 216 is arranged to shift skipped working chambers between different modes of operation. As previously noted, skip fire engine operation involves firing one or more selected working cycles of selected working chambers and skipping others. In a first mode of operation, the skipped working chambers are deactivated during skipped working cycles—i.e., for the duration of the corresponding working cycle, very little or no air is passed through the corresponding working chamber. This mode is achieved by deactivating the intake and/or exhaust valves that allow air ingress and egress into the working chamber. If both intake and exhaust valves are closed, gases are trapped in the working chamber effectively forming a pneumatic spring.

In a second mode of operation, the intake and exhaust valves for the skipped working chamber are not sealed during the corresponding working cycle and air is allowed to flow through the working chamber. In this mode of operation no combustion takes place in the skipped working chamber and the air pumped through the skipped working chamber is delivered to the exhaust system. This has the effect of diluting the exhaust stream and lowering its temperature. It also introduces excess oxygen into the exhaust stream.

In a third mode of operation, the intake and exhaust valves of a skipped working chamber open and fuel is injected into the cylinder late in the power stroke. The result is uncombusted or only slightly combusted fuel in the exhaust stream delivered by the skipped working chambers. The uncombusted hydrocarbons enter the oxidizing catalytic converter and react exothermically with the air from the skipped working chambers. This reaction helps to heat the oxidizing catalytic converter. Such an approach can be particularly useful during an engine start-up period in which the oxidizing catalytic converter needs to be rapidly heated in order to minimize the emission of pollutants. In other embodiments, the uncombusted hydrocarbons may be useful to clean a particulate filter 104 by raising its temperature to burn off accumulated soot. While deliberating introducing hydrocarbons into the exhaust system may be useful in some situations, this practice should be generally avoided or minimized, since it reduces fuel economy.

It should be appreciated that the skipped cylinders can be operated in any of the three modes of operation, i.e. deactivated, operating valves without fuel injection, or injecting fuel in a manner that results in little or no combustion. That is on some working cycles a skipped cylinder may be operated with disabled valves and on a subsequent cycle with operating valves and on a following cycle with disabled valves. Whether a cylinder is skipped or fired is also controlled in a dynamic manner. This level of control allows optimization of the amount of air, oxygen, and uncombusted fuel delivered into the exhaust system by the skipped cylinders. The fired cylinders generally produce hot exhaust gases containing some residual oxygen, since the cylinders are generally running lean, as well as some residual level of unburned hydrocarbons.

Controlling emissions during engine start-up is technically challenging because the various aftertreatment elements have not reached their operating temperatures. Initially from a cold start all engine and exhaust components are cold. It may be desirable to start the engine at a relatively low firing fraction, with firing cylinders at a nominally stoichiometric air/fuel ratio, and keep all the skipped cylinders in mode one to avoid pumping any air into the oxidizing catalytic converter. Once the oxidizing catalytic converter temperature has started to rise, oxygen may be delivered to the catalytic converter by operating at least some of the skipped cylinders in the second or third mode. Unburned hydrocarbons may simultaneously be delivered to the oxidizing catalytic converter by running the firing cylinders at a rich air/fuel ratio or via late fuel injection through the skipped cylinders, i.e. mode three operation. The oxygen and unburned hydrocarbons may then exothermically react in the oxidizing catalyst converter to more rapidly increase its temperature. This reaction may occur only once the oxidizing catalyst converter is at or above hydrocarbon light-off temperature and thus it may be desirable to only introduce oxygen and unburned hydrocarbons to the catalytic converter once it has reached that temperature. Once the oxidizing catalytic converter has reached its operational temperature all the skipped cylinders may be operated in mode three, late fuel injection through the skipped cylinders, to raise the exhaust gas temperature. It should be appreciated that heating the oxidizing catalyst by supplying it with unburned fuel and oxygen will also heat other aftertreatment elements downstream in the exhaust system from the oxidizing catalyst. These aftertreatment elements may include the reducing catalyst and/or particulate filter.

In various implementations, the power train parameter adjusting module 216 is arranged to cause the engine to shift between the three modes of operation based on the aftertreatment element temperature data and/or other engine operating parameters. For example, in some approaches, if the engine controller determines that the temperature of the aftertreatment element is below its effective operating temperature range, but above the light-off temperature, (e.g., during a cold start or under extended low load conditions), the power train parameter adjusting module may utilize the third mode of operation (e.g., a skip fire engine operation that involves the delivery of unburned hydrocarbons to the oxidizing catalytic converter). This mode of operation can help expedite the heating of the oxidizing catalyst to a desired operating temperature. If, however, the engine controller determines that the temperature of the oxidizing catalyst is high enough or has reached an effective operating temperature range temperature, the power train parameter adjusting module will shift to the first mode of operation (e.g., skip fire engine operation involving delivery of a lean air fuel mixture to the fired working chambers and deactivation of the skipped working chambers.)

There also may be situations in which the catalyst temperature is too high and cooling is required. For example, compression ignition engines are typically coupled with an aftertreatment emission control element that operates in a somewhat narrower band of operating temperatures than spark ignition engines. In some cases, the temperature of the aftertreatment element may exceed this band. It is desirable to avoid such situations, since excessive temperatures can damage or impair the performance of the aftertreatment element. Accordingly, in some embodiments, the engine controller makes a determination as to whether the aftertreatment element has exceeded a particular threshold temperature. If that is the case outside air may be injected into the exhaust system prior to any aftertreatment element whose temperature exceeds its operational temperature range. The extra air that flows through the exhaust system will help cool the aftertreatment emission control element. Once the engine controller determines that the temperature of the aftertreatment element is within a desired operating temperature band, the outside air injection may be terminated.

It should be appreciated that in some embodiments, different modes may be applied to different working cycles. In other words, during a selected working cycle of a particular working chamber, the working chamber may be operated in a second mode while in the very next working cycle, the corresponding working chamber will be operated in a first mode. In other words, in one working cycle, the skipped working chamber may allow for the passage of air, while in the very next firing opportunity that involves a skipped working chamber, the working chamber is deactivated and sealed. Changes in the delivery of air-fuel mixtures and the operation of the working chamber valves can change dynamically from one working cycle to the next and from one working chamber to the next in response to the exhaust system temperature data and/or a variety of engine operating parameters.

The firing timing determination unit 204 receives input from the firing fraction calculator 206 and/or the power train parameter adjusting module 216 and is arranged to issue a sequence of firing commands (e.g., drive pulse signal 213) that cause the engine to deliver the percentage of firings dictated by the commanded firing fraction 223. The firing timing determination unit 204 may take a wide variety of different forms. For example, in some embodiments, the firing timing determination unit 204 may utilize various types of lookup tables to implement the desired control algorithms. In other embodiments, a sigma delta converter or other mechanisms are used. The sequence of firing commands (sometimes referred to as a drive pulse signal 213) outputted by the firing timing determination unit 204 may be passed to a firing control unit 240 which orchestrates the actual firings.

Some implementations involve selective firing of particular working chambers and not others. For example, during an engine startup period from a cold start, the engine controller may fire only a particular subset of working chambers that are physically closer to an aftertreatment element in the exhaust system, i.e have a shorter exhaust stream path to the aftertreatment element. Since exhaust from those working chambers has a shorter path to travel, the exhaust loses less thermal energy and can help heat the aftertreatment elements more quickly and efficiently. At least one working chamber may be deactivated such that no air is pumped through the working chamber raising the temperature of the exhaust gases for a number of working cycles. This at least one deactivated working chamber may be the working chamber positioned farthest from the aftertreatment elements being heated.

The engine controller 200, firing fraction calculator 206, the power train parameter adjusting module 216, and the firing timing determination unit 204 may take a wide variety of different forms and functionalities. For example, the various modules illustrated in FIG. 3 may be incorporated into fewer components or have their features performed by a larger number of modules. Additional features and modules may be added to the engine controller. By way of example, some suitable firing fraction calculators, firing timing determination units, power train parameter adjusting modules and other associated modules are described in co-assigned U.S. Pat. Nos. 7,954,474; 7,886,715; 7,849,835; 7,577,511; 8,099,224; 8,131,445; 8,131,447; 9,086,020; and 9,120,478: U.S. patent application Ser. Nos. 13/774,134; 13/963,686; 13/953,615; 13/886,107; 13/963,759; 13/963,819; 13/961,701; 13/843,567; 13/794,157; 13/842,234; 13/004,839, 13/654,244 and 13/004,844, each of which is incorporated herein by reference in its entirety for all purposes. Any of the features, modules and operations described in the above patent documents may be added to the controller 200. In various alternative implementations, these functional blocks may be accomplished algorithmically using a microprocessor, ECU or other computation device, using analog or digital components, using programmable logic, using combinations of the foregoing and/or in any other suitable manner.

FIG. 4 shows exhaust manifold gas temperature versus engine operating load for a representative boosted, compression ignition engine operating at 1250 rpm with skip fire control. The engine operating load is expressed in BMEP relative to the total engine displacement with all cylinders operating. A plurality of operating curves 410 a thru 410 j are shown in FIG. 4. These correspond to operating the engine with different firing fractions with deactivated cylinders, operational mode one described above. The left most curve 410 a corresponds to the lowest firing fraction and the right most curve 410 j corresponds to the highest firing fraction, i.e. a firing fraction of 1, all cylinders firing. Intermediate curves 410 b thru 410 i correspond to successive higher firing fractions. Curve 410 j, corresponding to a firing fraction of one, is identical to the corresponding portion of curve 280 shown in FIG. 2. The firing fractions chosen may correspond to firing fractions providing acceptable NVH (noise, vibration, and harshness) characteristics as described in co-assigned U.S. Pat. No. 9,086,020 and pending U.S. patent application Ser. Nos. 13/963,686 and 14/638,908. Also shown in FIG. 4 is the shaded region 270 which depicts the exhaust manifold gas temperature required to elevate an aftertreatment element in the exhaust system into its operational temperature range. This region is identical to the shaded region 270 shown in FIG. 2.

Within the allowed operating region the required engine output can be generated by operating on one of the firing fractions denoted in curves 410 a thru 410 j while maintaining the engine exhaust gas temperature within the required temperature limits. In some cases several firing fractions may deliver acceptable engine output and exhaust gas temperature. In these cases the firing fraction providing the most fuel efficient operation may be selected by the firing fraction calculator 206 (FIG. 3) to operate the engine. Inspection of FIG. 4 shows that the allowed steady-state operating range using skip fire control is much larger than the corresponding range without such control as shown in FIG. 2. Similar operating curves 410 a thru 410 j and exhaust manifold gas temperature ranges 470 can be generated for other engine speeds. Generally operation in skip fire control with varying firing fractions will allow steady-state operation over a wide range of engine loads.

As shown in FIG. 4 there is a range of high load conditions, above approximately 9.5 bar BMEP, where the engine cannot operate in steady-state and maintain the element in the aftertreatment system in its desired temperature range. These high loads require operation on all cylinders and thus no cylinders are skipped, i.e. a firing fraction of one. Under these conditions the aftertreatment system temperature may be reduced by injecting outside air into the exhaust system as previously described. Also, under typical driving cycles an engine seldom operates in this high load region over extended periods of time. Operation for a short time period in this high load regime, such as when passing or going up a steep hill, will generally not result in the aftertreatment system exceeding its operating temperature range due to the thermal inertia of the aftertreatment system. In these cases no outside cooling need be applied to the aftertreatment system, since it will not exceed its operating temperature range.

Operation of a compression ignition internal combustion with skip fire control and deactivating the skipped cylinders allows maintaining a high exhaust gas temperature over a large engine operating range. High exhaust gas temperatures are generally advantageous for a particulate filter (104 in FIGS. 1A and 1B), which may be part of an aftertreatment system. Maintaining the particulate filter 104 at a high temperature will encourage oxidization of soot particles trapped in the filter.

Some particulate filters 104 require their temperature to be raised, periodically, to around 500 C to 600 C to remove accumulated soot on the filter in order for the filter to function again. This active temperature management process is very fuel consuming. Even though the clean-out/regeneration process has to occur every 200 to 400 miles, depending on size of filter, the overall penalty on fuel economy can be significant. Skip fire operation may reduce or eliminate the need for regeneration where the particulate filter 104 is heated to fully oxidize soot trapped in the filter thus cleaning the filter. With skip fire operation the particulate filter can generally operate at a higher temperature, which reduces the soot build up rate lengthening the period between cleaning cycles. In some cases, skip fire control may be used to temporarily deliberately raise the exhaust stream temperature to clean the particulate filter 104 in an active regeneration process. Such a cleaning method will be more fuel efficient than cleaning methods that rely on introducing uncombusted hydrocarbons into the exhaust stream.

FIG. 5 shows exhaust manifold gas temperature versus engine operating load for a representative boosted, compression ignition engine operating at 1250 rpm with skip fire control. FIG. 5 is similar to FIG. 4 except the skipped cylinders are not deactivated, they are pumping air without any added fuel (mode 2). The various curves 510 a-510 j represent operation at different firing fractions. The numeric designators 510 a thru 510 j represent the same firing fractions as shown in FIG. 4. Curve 510 j, which corresponds to operation with a firing fraction of one, is identical to curve 410 j and curve 280. This is operational mode two as described above. Shaded region 270 is identical to that shown in FIG. 2 and FIG. 4 and represents the exhaust gas temperature required to heat an element in the aftertreatment system into its operational temperature range. Inspection of FIG. 5 shows that operation in mode two without adding fuel to the skipped cylinders does little to expand the range of allowable steady-state operating conditions relative to all cylinders firing (shown in FIG. 2). Operation of some skipped cylinders in mode 2, pumping, and some skipped cylinders in mode 1, deactivated, may be useful to control exhaust gas temperature in some cases.

Two operating areas where skip fire control is particularly useful are during start-up and at light loads where a compression ignition engine usually runs very lean. This is because the fuel flow is very low as result of the light load. In most older compression ignition engines the air flow cannot be further reduced since these engines generally have no throttle. Therefore, the exhaust temperature can sometimes be too low for effective NO_(x) conversion in the catalyst. Some prior art solution have used hydrocarbon injection into the exhaust system to generate additional heat in the exhaust system maintaining one or more aftertreatment elements in their desired operational temperature range. This control method sacrifices fuel economy. Use of skip fire control may obviate—or at least significantly reduce—the need for this hydrocarbon injection.

FIG. 6 shows the temperature of an aftertreatment element 606 over cold start-up and a portion of a drive cycle of a prior art compression ignition engine. The figure also shows the light-off temperature 602, the temperature at which some hydrocarbons in the exhaust stream will self-ignite, and the lower boundary of the effective operating range of the aftertreatment element 604. In this figure the light-off temperature is shown as 150 C and the lower aftertreatment operating range as 200 C; however, these should be treated as only representative values and in practice they may be larger or smaller.

The drive cycle begins with the aftertreatment element at ambient temperature, assumed to be 20 C. The aftertreatment element reaches light-off temperature at time t₁. It is only after this time that injecting hydrocarbons into the exhaust stream can raise the temperature of an aftertreatment element. The aftertreatment element temperature continues to rise until time t₂ where it reaches its effective operating range. Prior to time t₂ the aftertreatment element is ineffective at removing pollutants from the exhaust stream. The aftertreatment element remains effective at removing pollutants until time t₃, which represents an extended low load portion of the drive cycle. For the period between t₃ and t₄ the aftertreatment element is below its operating range and is ineffective at removing pollutants.

To reduce emissions, it is desirable to reduce the start-up time until the aftertreatment element reaches its operating temperature and reduce or eliminate the aftertreatment element falling below its operating temperature during low load conditions. FIG. 7 shows a representative drive cycle using the current invention. The prior art aftertreatment element temperature is shown as the dotted line 606, which is identical to the aftertreatment temperature shown in FIG. 6. The light-off temperature 602 and lower limit of the aftertreatment element operating temperature 604 are as in FIG. 6. Curve 608 depicts the aftertreatment element temperature. The time for the aftertreatment element to reach its operating temperature has been reduced from t₂ to t_(2′). Also, the aftertreatment element is maintained within its effective operating range in the extended low load period between t₃ and t₄. The engine controller may maintain the aftertreatment element temperature somewhat above its minimum operating temperature range to maintain a buffer above this value. Maintaining a buffer helps to prevent the aftertreatment element temperature from falling below its operating range should the engine load be further reduced. Engine emissions over the drive cycle are thus lower when using the current invention shown in FIG. 7 as compared to the prior art shown in FIG. 6.

The invention has been described primarily in the context of controlling the firing of 4-stroke, compression ignition, piston engines suitable for use in motor vehicles. The compression ignition may use a stratified fuel charge, a homogeneous fuel charge, partial homogeneous charge, or some other type of fuel charge. However, it should be appreciated that the described skip fire approaches are very well suited for use in a wide variety of internal combustion engines. These include engines for virtually any type of vehicle—including cars, trucks, boats, construction equipment, aircraft, motorcycles, scooters, etc.; and virtually any other application that involves the firing of working chambers and utilizes an internal combustion engine.

In some preferred embodiments, the firing timing determination module utilizes sigma delta conversion. Although it is believed that sigma delta converters are very well suited for use in this application, it should be appreciated that the converters may employ a wide variety of modulation schemes. For example, pulse width modulation, pulse height modulation, CDMA oriented modulation or other modulation schemes may be used to deliver the drive pulse signal. Some of the described embodiments utilize first order converters. However, in other embodiments higher order converters or a library of predetermined firing sequences may be used.

In other embodiments of the invention, intake and exhaust valve control may be more complex than simple binary control, i.e. open or closed. Variable lift valves may be used and/or the valve opening/closing timing may be adjusted by a cam phaser. These actuators allow limited control of cylinder MAC without use of a throttle and its associated pumping losses. Advantageously adjustment of the cylinder MAC allows control of the fuel/air stoichiometry for a fixed fuel charge. The combustion conditions may then be optimized for improved fuel efficiency or to provide desired conditions, i.e. oxygen level, temperature, etc., in the combustion exhaust gases.

Although only a few embodiments of the invention have been described in detail, it should be appreciated that the invention may be implemented in many other forms without departing from the spirit or scope of the invention. For example, the drawings and the embodiments sometimes describe specific arrangements, operational steps, and control mechanisms. It should be appreciated that these mechanisms and steps may be modified as appropriate to suit the needs of different applications. For example, the order of the various aftertreatment emission control elements in the exhaust path shown in FIGS. 1A and 1B may be altered. Additional aftertreatment devices may be use and the functionality of individual elements combined into a single element. The methods of performing the oxidization and reduction steps may be altered; for example, a lean NO_(x) trap may be used in place of the SCR catalyst. Using a NO_(x) adsorber/NO_(x) trap for a lean burn engine requires the engine to run slightly rich periodically, such as every minute or two, to purge the NO_(x) from the adsorber, regenerating the NO_(x) trap. Since compression ignition engines typically operate under very lean conditions, especially at light loads, to operate the engine under rich condition to purge the NO_(x) trap requires a significant reduction in air flow through the engine, which normally requires throttling the engine air flow. The regeneration process is also a very fuel consuming. It would be very advantageous to use skip fire control to purge a NO_(x) trap compared to traditional methods of purging NO_(x) traps. Use of skip fire control may obviate the requirement to have a throttle in the engine, reducing engine cost and complexity. In other embodiments, use of skip fire control may be used in concert with an engine throttle to control exhaust gas temperature.

Additionally, while the invention has been generally described in terms of a compression ignition engine, it may also be used in spark ignition, spark ignition assisted, or glow plug ignition assisted engines. In particular, the invention is applicable to lean burn spark ignition engines. These engines have some of the attributes of compression ignition engines, such as oxygen in the exhaust stream, so they cannot generally use a conventional 3-way catalyst based aftertreatment system. In some embodiments not all of the cylinders in an engine need be capable of deactivation. This may reduce costs relative to an engine having all cylinders capable of deactivation. In some embodiments, one or more of the described operations are reordered, replaced, modified or removed. Therefore, the present embodiments should be considered illustrative and not restrictive and the invention is not to be limited to the details given herein. 

1. A method of reducing accumulated soot in a particulate filter utilized in an exhaust path of a lean burn internal combustion engine having a plurality of working chambers, each working chamber being configured to operate in a series of successive working cycles, the method comprising: during operation of the lean burn internal combustion engine, transitioning to a particulate filter cleaning mode, in which the lean burn internal combustion engine is operated in a skip fire mode to increase the temperature of exhaust gases sufficiently to raise the temperature of the particulate filter sufficiently to oxidize and thereby remove soot accumulated on the particulate filter, wherein during operation in the skip fire mode, combustion is caused to occur in selected fired working cycles and no combustion is caused to occur in selected skipped working cycles; deactivating the corresponding working chambers during at least some of the skipped working cycles to prevent air from passing through such working chambers during such skipped working cycles; and wherein during operation in the skip fire mode at a first effective displacement, at least one of the working chambers is sometimes skipped and sometimes fired.
 2. A method as recited in claim 1 wherein the particulate filter is heated to a temperature in the range of approximately 500° C. to 600° C.
 3. A method as recited in claim 1 wherein the corresponding working chambers are deactivated during all of the skipped working cycles.
 4. A method as recited in claim 1 wherein late fuel injection is utilized in some of the skipped working cycles to cause unburnt hydrocarbons to be introduced into the exhaust path, wherein the unburnt hydrocarbons are oxidized to help heat the particulate filter.
 5. A method as recited in claim 1 wherein at least some of the fired working cycles utilize an air/fuel ratio that is sufficiently rich to cause unburnt hydrocarbons to be introduced into the exhaust path, wherein the unburnt hydrocarbons are oxidized to help heat the particulate filter.
 6. A method as recited in claim 1 wherein the lean burn internal combustion engine is a Diesel engine.
 7. A method as recited in claim 1 wherein the lean burn internal combustion engine is a boosted engine.
 8. A method as recited in claim 7 wherein the boosted engine is a turbocharged engine.
 9. A method as recited in claim 1 wherein an output of the lean burn internal combustion engine is controlled at least in part by an exhaust gas recirculation system.
 10. A method as recited in claim 1 wherein some of the plurality of working chambers of the internal combustion engine are capable of deactivation and some of the plurality of working chambers of the internal combustion engine are incapable of deactivation. 11.-20. (canceled)
 21. A vehicle, comprising: a lean burn internal combustion engine having a plurality of working chambers, each working chamber configured to operate in a series of successive working cycles; a particulate filter included in an exhaust path that is fluidly coupled to the lean burn combustion engine; and engine controller arranged to selectively operate the lean burn internal combustion engine in both: (a) a skip fire mode where at least one working chamber over successive working cycles is (i) fired causing a combustion event, (ii) skipped resulting in no combustion event and (iii) either fired or skipped causing a combustion or no combustion event respectively; and (b) a particulate filter cleaning mode in which the lean burn internal combustion engine is operated so that air is prevented from passing through one or more of the skipped working cycles in the skip fire mode, causing gases exhausted from the lean burn internal combustion engine to sufficiently rise in temperature in the exhaust pathway, oxidizing and thereby removing soot accumulation on the particulate filter.
 22. The vehicle as recited in claim 21, wherein soot is removed from the particulate filter when heated in the range of approximately 500° C. to 600° C.
 23. The vehicle as recited in claim 21 wherein the air is prevented from passing through the one or more working chambers during skipped working cycles by (a) closing an intake valve, (b) closing an exhaust valve or (c) both (a) and (b) associated with the one or more skipped working chambers respectively.
 24. The vehicle as recited in claim 21, further comprising: a fuel injection system arranged to inject fuel into the plurality of working chambers of the lean burn internal combustion engine; wherein the fuel injection system is arranged to selectively implement late fuel injection, whereby the fuel is injected late in a power stroke of select working cycles of the working chambers, causing unburnt hydrocarbons to be introduced into and oxidized in the exhaust path, which contributes to heating the particulate filter.
 25. The vehicle as recited in claim 21 wherein at least some of the fired working cycles of the working chambers utilize an air/fuel ratio that is sufficiently rich to cause unburnt hydrocarbons to be introduced into the exhaust path, wherein the unburnt hydrocarbons are oxidized to contribute to heating the particulate filter.
 26. The vehicle as recited in claim 21 wherein the lean burn internal combustion engine is a Diesel engine.
 27. The vehicle as recited in claim 21 wherein the lean burn internal combustion engine is a boosted engine.
 28. The vehicle as recited in claim 27 wherein the boosted engine is a turbocharged engine.
 29. The vehicle as recited in claim 21, further comprising an exhaust gas recirculation system, wherein an output of the lean burn internal combustion engine is at least controlled by the exhaust gas recirculation system.
 30. The vehicle as recited in claim 21 wherein at least one of the plurality of working chambers of the lean burn internal combustion engine is capable of deactivation and at least a second one of the plurality of working chambers of the internal combustion engine is incapable of deactivation. 